Rear wheel sprocket arrangement

ABSTRACT

A plurality of sprockets which are coaxial with respect to a sprocket rotation axis, are arranged with axial spacing from each other and have different numbers of teeth which are constructed for positive-locking engagement with a bicycle chain. The pinion arrangement has a gear range quotient which is formed by division of the number of teeth of the sprocket having the largest diameter by the number of teeth of the sprocket having the smallest diameter, and has a packing density quotient which is formed by division of the number of sprockets in the sprocket arrangement by the axial spacing measured in millimeters of the axially outermost pinions from each other. The pinion arrangement may have a gear range packing coefficient, formed from the product of the gear range quotient and the packing density quotient, which is greater than 1.25.

This application is a Continuation of U.S. Utility patent applicationSer. No. 15/085,570, filed Mar. 30, 2016, which claims priority toand/or the benefit of German Patent Application No DE 10 2015 205 736.4,filed on Mar. 30, 2015 the contents of which are included by referencein their entirety.

FIELD OF THE INVENTION

The invention relates to a bicycle rear wheel sprocket arrangement whichcan be rotated about a sprocket rotation axis, comprising a plurality ofsprockets which are coaxial with respect to the sprocket rotation axis,are arranged with axial spacing from each other, and have differentnumbers of teeth which are constructed for positive-locking engagementwith a bicycle chain.

BACKGROUND

Bicycle rear wheel sprocket arrangements are generally known as bicyclecomponents. They are used, for example, in the tourer bicycles, racingbicycles and in the mountain bike sectors at locations where derailleurmechanism gears are provided in bicycles in order to bring aboutdifferent transmission ratios from the tread crank to the rear wheel. Inthis instance, the number of sprockets on the rear wheel has increasedover time in order to graduate transmission ratios more and more finely.This fineness of the graduation was even further supported by anincreasing number of chain rings on the tread crank.

Recently, there has been perceived a development tendency which againreduces the number of chain rings which are directly connected to thetread crank. This may lead to singular derailleur mechanisms in whichonly a single chain ring is provided on the tread crank. With thereduction in the number of chain rings, the number of sprockets in therear wheel sprocket arrangement and the tooth number graduation thereofassumes increasing importance for producing desired transmission ratios.

Reference may be made to the publication U.S. Pat. No. 3,748,916 A ofMorse by way of example of a bicycle rear wheel sprocket arrangement ofthe generic type for a single derailleur mechanism. This publicationdiscloses a bicycle rear wheel sprocket arrangement with a total of 5sprockets, of which the smallest may have 9 and the largest may have 45teeth. Consequently, that sprocket arrangement has a gear range quotientof 45:9=5. Consequently, the gear range quotient is a measurement forthe bandwidth of transmission ratios which can be produced with asprocket arrangement. The greater the value of the gear range quotient,the greater the bandwidth of transmission ratios which can be produced.

The technically most advanced prior art in the field of singlederailleur mechanisms may currently be a system which is marketed bySRAM under the name “XX1”. This system with a rear wheel sprocketarrangement comprising 11 sprockets has a gear range quotient of 4.2.

Reference is further made as additional prior art to EP 2 022 712 A ofCampagnolo, which discloses a 12 sprocket arrangement whose smallestsprocket has 11 teeth and whose largest sprocket has 27 teeth. The gearrange quotient of that sprocket arrangement is, at 2.45, slightly lessthan half as large as that of the sprocket arrangement of the previouslydiscussed US patent.

Reference may be made to U.S. Pat. No. 5,954,604 A as another extremeexample of a multiple sprocket arrangement which sets out a sprocketarrangement having 14 sprockets. FIG. 13 of this publication shows anembodiment in which the smallest sprocket of the sprocket arrangementhas 11 teeth and the largest sprocket has 39 teeth. Therefore, the gearrange quotient of that known sprocket arrangement is 3.54.

In a more comprehensible manner, the number of sprockets in the sprocketarrangement gives a measurement of the fineness of the graduation of thetransmission ratios which can be achieved with a rear wheel sprocketarrangement. The higher the number of sprockets, the finer thegraduation of the adjustable transmission ratios can be.

However, there is only limited structural space available for thearrangement of the rear wheel sprocket arrangement on a rear wheel hub.Because of this limited structural space the number of sprockets in thesprocket arrangement cannot be freely increased. Therefore, the packingdensity quotient mentioned in the introduction directly gives ameasurement of how effectively the structural space present on the rearwheel hub is used for the arrangement of sprockets. Indirectly, thepacking density quotient is also a measurement concerning the finenessof the graduation of the achievable transmission ratios because itcontains in the numerator information relating to the number ofsprockets in the rear wheel sprocket arrangement. Again, the followingapplies: the higher the packing density quotient, the more effective isthe use of structural space for the arrangement of sprockets. Similar tothe gear range quotient, the packing density quotient is a dimensionlessnumerical value, for the establishment of which only the numerical valueof the spacing measured in millimeters (“mm”) between the axiallyoutermost sprockets should be used.

The 5 sprocket arrangement known from U.S. Pat. No. 3,748,916 A takesup, for example, an axial structural space of approximately 26 mm.Consequently, the packing density quotient purely as a numerical valuevariable of this sprocket arrangement is 0.192.

In comparison, EP 2 022 712 A for the 12 sprocket arrangement, theimplementation of which is not demonstrated in the publication, however,sets out an axial structural space requirement of 40.5 mm. This resultsin a packing density quotient of 0.296.

The above-mentioned single derailleur system “XX1” of the same Applicanthas, with 11 sprockets in a structural space of 38.4 mm, a packingdensity quotient of 0.286.

Finally, reference may be made as an additional comparison to theabove-mentioned U.S. Pat. No. 5,954,604 A in which 14 sprockets of asprocket arrangement are received with an axial spacing of the outermostsprockets which axially measures approximately 50 mm, which results in apacking density quotient of approximately 0.28.

As evidenced herein, modern rear wheel sprocket arrangements have apacking density quotient of slightly below 0.3. This sets out thecurrent state of axial structural space use on rear wheel hubs.

SUMMARY AND DESCRIPTION

In an embodiment, a bicycle rear wheel sprocket arrangement which can berotated about a sprocket rotation axis includes a plurality of sprocketswhich are coaxial with respect to the sprocket rotation axis and arearranged with axial spacing from each other and have different numbersof teeth which are constructed for positive-locking engagement with abicycle chain. The plurality of sprockets having a gear range quotientwhich is formed by division of the number of teeth of a sprocket of theplurality of sprockets having the largest diameter by the number ofteeth of a sprocket of the plurality of teeth having the smallestdiameter. The plurality of sprockets also having a packing densityquotient which is formed by division of the number of sprockets in thesprocket arrangement by the axial spacing measured in millimeters of theaxially outermost sprockets from each other. The plurality of sprocketsmay have a gear range packing coefficient, formed from the product ofthe gear range quotient and the packing density quotient, which isgreater than 1.25.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a longitudinal sectioned view of an embodiment according tothe invention of a bicycle rear wheel sprocket arrangement in a plane ofsection which contains the sprocket rotation axis;

FIG. 2 is an axial front view of the sprocket arrangement of FIG. 1;

FIG. 3 is an axial rear view of the sprocket arrangement of FIGS. 1 and2;

FIG. 4 is an axial view of the sprocket having the smallest diameter ofthe sprocket arrangement of FIGS. 1 to 3;

FIG. 5 is a longitudinal sectioned view through the sprocket having thesmallest diameter of FIG. 4 along the plane of section V-V whichcontains the sprocket rotation axis; and

FIG. 6 is a longitudinal sectioned view through the sprocket having thesmallest diameter of FIG. 4 along the plane of section VI-VI whichcontains the sprocket rotation axis.

DETAILED DESCRIPTION OF THE DRAWINGS

A bicycle rear wheel sprocket arrangement can be rotated about asprocket rotation axis, comprising a plurality of sprockets which arecoaxial with respect to the sprocket rotation axis. The sprockets arearranged with axial spacing from each other and have different numbersof teeth which are constructed for positive-locking engagement with abicycle chain. The sprocket arrangement may have a gear range quotientwhich is formed by division of the number of teeth of the sprockethaving the largest diameter by the number of teeth of the sprockethaving the smallest diameter. The sprocket arrangement may have apacking density quotient which is formed by division of the number ofsprockets in the sprocket arrangement by the axial spacing measured inmillimetres of the axially outermost sprockets from each other.

During the establishment of the packing density quotient, an importantaspect is the manner in which the axial spacing of the axially outermostsprockets from each other is established. This axial distance is,generally, an axial distance between the sprocket having the largestdiameter and the sprocket having the smallest diameter. In principle, itis possible to use the sprocket center planes which are orthogonal tothe sprocket rotation axis as reference planes for establishing thespacing.

For the production of switching operations in the rear wheel sprocketarrangement, the positioning of the ratchet gears relative to the rearwheel sprocket arrangement is orientated with respect to the front facesof the individual sprockets. The front faces of the sprockets aredirected away from the bicycle longitudinal center plane in theassembled state, however, the axial front faces of the individualsprockets are preferably used as reference faces for establishing thespacing. In this instance, the front face should be used at the sprockethaving the largest diameter at the side which the next-smallest sprocketis opposite. At the sprocket having the smallest diameter, the frontface which is directed away from the sprocket having the largestdiameter should be used. If a sprocket is provided with an angledportion at the rear wheel hub for reasons of the most effective usepossible of the structural space provided for the fitting thereof, thefront face portion nearest the tooth ring of the sprocket should bedecisive. Therefore, the spacing of the axially outermost sprockets fromeach other is preferably the axial spacing of the front faces of thosesprockets from each other.

In the case of doubt as to what should be determined as the front face,the face or face portion of a sprocket with which the sprocket at therelevant side is positioned on a planar level is a front face of thesprocket. If the sprocket has individual teeth which project axiallybeyond the front face—for instance, acting as switching supportteeth—those teeth should not be taken into consideration when the frontface is established. Such “exceptional teeth” which project axiallybeyond the front face are known, for example, from EP 1 671 880 A.

The overview set out above of different existing rear wheel sprocketarrangements shows that existing sprocket arrangements either offer alarge bandwidth of transmission ratios, but they are then graduated in arelatively coarse manner and distributed over a relatively large axialstructural space, or the existing sprocket arrangements offer a veryfine graduation of relatively narrow bandwidths of transmission ratios,but then with very effective use of the axial structural spaceavailable.

The existing sprocket arrangements for bicycle rear wheels may no longercomply in each case with the increasing demands placed on them. In viewof the most recent technical trends in the development of bicyclecomponents, it is no longer sufficient to graduate bandwidth oftransmission ratios only in a very coarse manner or to offer only asmall bandwidth of transmission ratios. In particular, but not only, inthe case of a single derailleur mechanism having only one chain ring, alarge bandwidth of transmission ratios which is graduated in arelatively fine manner and which has space in conventional bicycleconstructions is required on the rear wheel. For this purpose, a newclass of bicycle rear wheel sprocket arrangements is required.

The embodiments presented herein meet these requirements on modernbicycle rear wheel sprocket arrangements by providing a bicycle rearwheel sprocket arrangement of the type mentioned in the introductionwhich has a gear range packing coefficient which is greater than 1.25.

In this instance, the gear range packing coefficient is the product ofthe gear range quotient and packing density quotients already discussedabove. The gear range packing coefficient is a measurement for whichbandwidth of transmission ratios is provided, with what graduation foruse in the axial structural space on the rear wheel hub. The higher thegear range packing coefficient is the greater is the bandwidth oftransmission ratios. Also, the finer is the graduation of thisbandwidth, the less axial structural space is required for using thesprocket arrangement.

By way of comparison, the gear range packing coefficient of the sprocketarrangement known from U.S. Pat. No. 3,748,916 A is approximately 0.96.The gear range packing coefficient of the 12 sprocket arrangement knownfrom EP 2 022 712 A is approximately 0.72. The gear range packingcoefficient of the rear wheel sprocket arrangement which is known fromU.S. Pat. No. 5,954,604 A, and which has 14 sprockets, is approximately0.991.

The gear range packing coefficient of the above described “XX1” systemis 1.20.

With the new class of rear wheel sprocket arrangements, in which thegear range packing coefficient is greater than 1.25, it is possible toprovide on rear wheel sprocket arrangements large bandwidths oftransmission ratios with a large number of sprockets in a small axialstructural space in a manner graduated relatively finely. Therefore, thegear range packing coefficient of a sprocket arrangement according toembodiments presented herein may be even greater than 1.3, particularlypreferably even greater than 1.35. It is easy to see that, withincreasing values of the coefficient discussed here, the ride comfortprovided by the relevant sprocket arrangements also increases withregard to transmission ratio bandwidth and graduation so that, inconjunction with tests carried out by the Applicant, sprocketarrangements having a gear range packing coefficient greater than 1.4are also available. As set out below with reference to a presentedembodiment, a gear range packing coefficient of 1.48 is provided.

With gear range packing coefficients greater than 1.25, a prerequisiteof reducing chain loads which occur during operation of a bicycle, moreprecisely chain tensile loads, is further met. Advantageous effects areconnected with the reduction of the chain tensile loads, such as areduction of the friction which acts within the bicycle chain or alsobetween the bicycle chain and an engagement element (e.g. a sprocket ora chain ring), and a reduction in resulting wear which occurs on thebicycle chain and engagement elements. Furthermore, a reduction of themaximum chain tensile load brings about a reduction of the deformationof the bicycle frame during operation as a result of chain tensile loadswhich change periodically with the turning of the tread crank.

Rear wheel sprocket arrangements with gear range packing coefficientsgreater than 1.25 are primarily achieved by using sprockets having thelargest diameter with very high numbers of teeth so that the load arm ofthose sprockets having the largest diameter is greater than the load armof comparable sprockets of existing and known sprocket arrangements. Forthe same torque introduced into the rear running wheel, a smaller force,that is to say, a smaller chain load, is required for the larger loadarm.

Rear wheel sprockets having a larger diameter allow the use of chainrings having a larger diameter, without the transmission ratio of thetread cranks with respect to the rear wheel being made worse. Quite thereverse: as a result of a sub-proportional increase of the diameter ofthe chain ring—in comparison, for instance, with existing singlederailleur systems—in relation to the increase of the diameter of thesprocket having the largest diameter, not only can the chain loadoccurring during operation be reduced but at the same time the bandwidthof the torque transmission from the tread cranks to the rear wheel canbe increased.

With increasing values of the gear range packing coefficient, structuralproblems with respect to the sprocket arrangements may have to besolved, which will be discussed in greater detail below. For example,the sprocket having the largest diameter may take up diameters at whichthe load applied to the sprocket by the bicycle chain results in anoteworthy flexural loading of the sprocket. This applies to an evengreater extent if the bicycle chain running on the sprocket having thelargest diameter may have a given oblique position relative to thebicycle longitudinal center plane because in an embodiment the sprockethaving the largest diameter is an axially innermost sprocket of thesprocket arrangement, whereas a front chain ring sprocket arrangementmay have a largest diameter sprocket at an axially outermost locationthus potentially causing a flexural loading of the rear sprocketarrangement when both such sprockets are engaged. Other chain engagementmay also cause flexural loading.

Similarly, an approach of the bicycle chain towards the next-largestsprocket up to abrasive contact of the chain with this sprocket may haveto be overcome on the sprocket having the smallest diameter, again as aresult of the oblique position of the bicycle chain running on thesprocket which has the smallest diameter. Such problems may arise, butare not common.

In order to provide the most adequate bandwidth of transmission ratiospossible in the bicycle rear wheel sprocket arrangement, it isadvantageous if the gear range quotient of the sprocket arrangement isgreater than or equal to 4.2. The greater the gear range quotient, thegreater the transmission ratio range provided by the sprocketarrangement. Therefore, the gear range quotient may be greater than orequal to 4.5.

In order to avoid difficulties of the sprocket arrangement duringoperation, such as, for example, those mentioned above, it may beadvantageous in some circumstances if the gear range quotient does notexceed the value 6. Difficulties during operation of the sprocketarrangement can be avoided with even greater probability if the gearrange quotient is not greater than 5.5.

The best possible use of the structural space available for receivingthe sprockets of the sprocket arrangement may be achieved if the packingdensity quotient of the sprocket arrangement has a value greater than orequal to 0.286. For the reasons mentioned, this value is preferablygreater than or equal to 0.290.

In conjunction with the sprocket arrangement as described by the packingdensity quotient, difficulties during operation of the sprocketarrangement can also occur with excessively high values of the packingdensity quotient, such as, for example, an undesirable contact of thebicycle chain which meshes with a sprocket with an adjacent sprocket,for instance because they have been moved axially together to anexcessive extent. In order to avoid such difficulties during operation,in some cases the packing density quotient should advantageously not begreater than 0.36, wherein the probability of avoiding operatingdifficulties is even greater at a packing density quotient which doesnot exceed 0.33.

In an embodiment, in able to provide the most advantageous possibletorque transmission from the tread crank to the rear running wheel toovercome gradients, the sprocket having the largest diameter of thesprocket arrangement may have 45 teeth or more. This takes intoconsideration a specific necessary minimum size of the front chain ring.Greater gradients can be overcome with a sprocket having the largestdiameter with at least 48 teeth. In the field of mountain bikes, asprocket having the largest diameter with at least 50 teeth may beadvantageous in order to overcome the challenges encountered by thecyclist.

With respect to hill climbing applications, the axial longitudinal endof the sprocket arrangement is used (i.e. the end that is nearer thesprocket having the largest diameter), and for fast riding a sprocket atthe opposite axial longitudinal end at which the sprocket having thesmallest diameter is located may be used. In order to be able to providetransmission ratios which are adequate to operate in cooperation withthe at least one chain ring on the tread crank, it is advantageouslyprovided that the sprocket having the smallest diameter does not havemore than 12 teeth, for example 12 or fewer teeth may be used. Highertravel speeds as a result of an even greater transmission of the musclepower into speed can be achieved by a sprocket having the smallestdiameter with no more than 11 teeth. In an embodiment, the sprockethaving the smallest diameter has no more than 10 teeth in order to beable to achieve high peak speeds.

In addition to the bandwidth of transmission ratios, the graduation ofthe bandwidth, which is provided in total by the rear wheel sprocketarrangement, is of interest. In view of the above-described greatbandwidth—expressed by the gear range quotient—the rear wheel sprocketarrangement discussed in this instance may offer at least eightadditional stages on the basis of an axially outermost sprocket so thatthe rear wheel sprocket arrangement according to the inventionpreferably has more than 8 sprockets. The fineness of the graduationalso increases with an increasing number of sprockets so that the rearwheel sprocket arrangement discussed in this instance has more than 10sprockets. In an embodiment the rear sprocket arrangement has more than11 sprockets.

In an embodiment, the percentage change of the number of teeth does notexceed 20% from one sprocket to the next-largest sprocket of the rearwheel sprocket arrangement, always in relation to the smaller of the twosprockets being considered. In an embodiment, the two largest percentagechanges in the number of teeth are brought about at the transition fromthe sprocket having the smallest diameter to the next-largest sprocketand at the transition from the second-largest sprocket to the sprockethaving the largest diameter. In an embodiment, the greatest percentageincrease in the number of teeth occurs at the transition from thesprocket having the smallest diameter to the next-largest sprocket. Thesecond-largest percentage change of the number of teeth may then be atthe transition from the second-largest sprocket to the sprocket havingthe largest diameter. In order to achieve the most uniform possiblegraduation of the achievable transmission ratios in the sprocket rangebetween the sprocket having the smallest diameter and the sprockethaving the largest diameter, it may further be advantageous if thepercentage changes in the number of teeth between two adjacent sprocketsof that sprocket group are not less than 12% and not more than 17%. Thevalue of the percentage change of the number of teeth from one sprocketto the next-largest sprocket of a sprocket arrangement may repeatedlydecrease initially and then increase again across the sprocketarrangement from the sprocket having the smallest diameter to thesprocket having the largest diameter.

In the above-discussed peripheral conditions for the sprocket having thelargest diameter, the sprocket may reach a relatively large mass and, ina manner connected therewith, a relatively great weight. Since thesprockets are part of the bicycle mass which is intended to beaccelerated and slowed, however, a sprocket having the largest diameterwith the smallest possible mass is desired. In order to ensure that themuscle power introduced by the cyclist at the tread crank can betransmitted to the rear running wheel in a reliable and durable manner,the sprocket having the largest diameter preferably has at the radiallyouter side a tooth ring region for transmitting force from the bicyclechain to the sprocket. Similarly, the sprocket having the largestdiameter preferably has at the radially inner side a hub region which isused to transmit torque from the sprocket to a rear wheel hub, at whichthe rear wheel sprocket arrangement is received. In order to reduce themass being moved, it is then advantageous if there are provided aplurality of sprocket spokes radially between the tooth ring region andthe hub region for the connection of those regions in a mannertransmitting torque.

In an embodiment, the sprocket having the largest diameter may beprovided with the smallest possible mass with dimensional stabilitywhich is adequate for operation if the sprocket having the largestdiameter has an outer spoke region which is located radially furtheroutwards and has an inner spoke region which is located radially furtherinwards. In this embodiment, the outer spoke region has a greater numberof sprocket spokes than the inner spoke region. For example, thesprocket spokes can be constructed in the inner spoke region so as tohave approximately the same cross-sectional area as the sprocket spokesin the outer spoke region.

In order to support the different number of sprocket spokes in the outerand inner spoke region, in an embodiment an intermediate ring regionwhich is solid in the peripheral direction may be constructed betweenthe outer and inner spoke region. The radially outer ends of thesprocket spokes of the inner spoke region and the radially inner ends ofthe sprocket spokes of the outer spoke region can be supported on thatsolid intermediate ring region.

In an embodiment, the above-mentioned tooth ring region is alsoconstructed to be solid, that is to say, without interruptions which cutout material on and/or between the teeth of the tooth ring region inorder to provide the most uniform conditions possible in a peripheraldirection for the torque transmission from the bicycle chain to thesprocket arrangement. In an embodiment, to achieve a more uniform torquetransmission from the sprocket arrangement to a rear wheel hub, theabove-mentioned hub region is also constructed in a solid manner.

In an embodiment, at least the sprocket having the largest diameter maybe constructed to have an angled portion. For example, the sprockethaving the largest diameter may be angled in such a manner that thetooth ring thereof has a greater axial spacing from the sprocket havingthe smallest diameter than an angled sprocket region of the sprockethaving the largest diameter, which sprocket region is located radiallyfurther inwards. This angled portion may provide, between the tooth ringregions of the axially outermost sprockets which are decisive for theswitching operation at the rear wheel sprocket arrangement, a greateraxial spacing than at the rear wheel hub for fitting the sprockets. Forreasons of stability, this angled portion may be configured in theradial portion of the solid intermediate ring region. In an embodiment,at least the angled portion may overlap with the intermediate ringregion in a radial direction. In another embodiment, the angled portionis located completely in the intermediate ring region.

Furthermore, the flexural stability of the sprocket having the largestdiameter may be increased by such an angled portion with respect tobending about a bending axis which is orthogonal to the rotation axis ofthe sprocket.

In an embodiment, the solid intermediate ring region is constructed tobe circular at least in a radial portion. For example, there may exist asolid radial portion of the intermediate ring region which has the sameradial spacing from the sprocket rotation axis at each point in aperipheral direction.

In order to reinforce the sprocket having the largest diameter, theremay further be provision for every second sprocket spoke acting as aconnection spoke with respect to the sprocket spoke thereof which isdirectly adjacent in a predetermined rotation direction to be connectedby a connection strut which is located radially between the longitudinalends of the sprocket spokes in the outer spoke region at least in aperipheral portion, preferably over the entire periphery. Consequently,pairs of sprocket spokes can be connected to each other by theconnection strut. In an embodiment, that connection strut may be used toconnect the sprocket having the largest diameter to the next-smallestsprocket which is axially directly adjacent. Therefore, there may beprovision for the arrangement of the at least one connection strutradially in a region which is radially overlapped by the axiallyadjacent, next-smallest, sprocket. This arrangement may be provided sothat the axially directly adjacent, next-smallest, sprocket hassufficient material for producing a physical connection with respect tothe connection strut on the sprocket having the largest diameter withoutimpairing the engagement of the bicycle chain with this sprocket as aresult of the physical connection.

It has been found that it is sufficient both for the requisiteadditional reinforcement of the sprocket which has the largest diameterand for an adequate physical connection of the sprocket having thelargest diameter with respect to the axially adjacent, next-smallestsprocket, if only every second sprocket spoke is constructed as aconnection spoke in the manner mentioned above. In order to obtain thelowest possible total weight of the sprocket having the largestdiameter, therefore, it is preferable for such a connection strut not tobe provided between the connection spoke and the sprocket spoke thereofwhich is adjacent in the rotation direction opposite the predeterminedrotation direction.

In an embodiment, a plurality of connection struts, and/or a majority ofconnection struts, preferably all the connection struts, are spacedapart from the sprocket rotation axis to the same extent.

As indicated above, the sprocket having the largest diameter can bephysically connected to the next-smallest sprocket in the region of theconnection struts. The connection struts proposed to this end may belocated on the sprocket having the largest diameter radially in a veryexternal position, for instance, radially slightly inside the tooth ringof the axially adjacent, next-smallest sprocket. The connection strutsare preferably arranged in the radially outermost third of the sprockethaving the largest diameter. The total radial extent of the sprockethaving the largest diameter is measured, in this embodiment, from thesprocket rotation axis to the radially outermost tooth tip even if thesprocket centrally has a recess.

The construction of the connection mentioned makes the operation of thesprocket having the largest diameter considerably easier because thephysical connection of the sprocket having the largest diameter to theaxially adjacent, next-smallest sprocket on the connection strutsincreases the flexural rigidity of the sprocket having the largestdiameter in the event of loading with bending about a bending axisorthogonal to the sprocket rotation axis.

In structural terms, the physical connection of the connection struts tothe next-smallest sprocket can be brought about by connections whichextend between a connection strut and the next-smallest sprocket so asto bridge the axial gap which exists between the sprocket having thelargest diameter and the next-smallest sprocket. The connections areconfigured so as to transmit torque both to the connection strut and tothe next-smallest sprocket. In an embodiment, in order to increase therigidity and dimensional stability of the bicycle rear wheel sprocketarrangement overall, the connections are configured so as to alsotransmit axial force both to the connection strut and to thenext-smallest sprocket.

In an embodiment, for effective transmission of torque from tread cranksto the sprocket having the largest diameter, the sprocket having thelargest diameter is constructed in such a manner that for at least onesprocket spoke, for example all the sprocket spokes of a spoke region orfor all the sprocket spokes, of the sprocket having the largestdiameter, the radially inner longitudinal end thereof leads the radiallyouter longitudinal end of the same sprocket spoke in a drive rotationdirection of the sprocket arrangement.

In an embodiment, in order to prevent undesirable shearing stress peaksand for the most uniform possible load distribution in the at least onesprocket spoke during the torque transmission, the at least one sprocketspoke is constructed to be curved about a curvature axis parallel withthe sprocket rotation axis so that it is curved in a concave manner whenviewed in a drive rotation direction and in a convex manner when viewedcounter to the drive rotation direction. The sprocket spokes of a spokeregion of the sprocket having the largest diameter are preferablyconstructed to be substantially identical—with the exception of theabove-mentioned connection spokes which are connected by means of aconnection web to the sprocket spoke directly adjacent in a rotationdirection.

In an embodiment, in order to increase the stability, in particulardimensional stability, of the sprocket arrangement, there may beprovision for the sprocket which is axially directly adjacent to thesprocket having the largest diameter to be constructed separately fromthe sprocket having the largest diameter but integrally with the axiallyadjacent sprocket at the side thereof directed away from the sprockethaving the largest diameter. The sprocket which is axially directlyadjacent to the sprocket having the largest diameter is preferablyconstructed integrally with a plurality of sprockets which are arrangedat the side thereof directed away from the sprocket having the largestdiameter.

In very general terms, it may be the case that two axially adjacentsprockets, in particular the sprocket having the largest diameter andthe sprocket which is axially directly adjacent thereto, are constructedseparately from each other and are connected so as to transmit torqueand/or axial force by a plurality of connection means which bridge theaxial gap existing between the adjacent sprockets. The connections maybe constructed as separate connection means separately from each of thetwo axially directly adjacent sprockets and may have been connected toeach of those sprockets. Alternatively or additionally, some or allconnection means may be constructed integrally with one of the twoaxially directly adjacent sprockets and may have been connected to theother sprocket.

A particularly solid and stable sprocket arrangement can be obtained inthat at least two axially directly adjacent sprockets, in particular asprocket smaller than the sprocket having the largest diameter and thesprocket which is axially directly adjacent thereto, are constructedintegrally with each other and are connected so as to transmit torqueand/or axial force by a plurality of connections or connection means inthe form of webs which bridge the axial gap existing between theadjacent sprockets. In this case, the webs may be constructed asconnections in an integral, materially cohesive, manner with respect toeach of the two axially directly adjacent sprockets. The webs may beformed, for example, by cutting methods, in particular by milling, fromthe piece of material forming the sprockets.

In an embodiment, the sprocket arrangement can be formed in a morestable manner the further the connections are arranged radiallyoutwards. The prerequisite for an arrangement of the connections in aposition which is as radially external as possible can be achieved whenthe connections are connected to the smaller of the two axially adjacentsprockets in a peripheral direction at a location at which a tooth islocated on the smaller of the two axially adjacent sprockets. Since thetooth projects radially further than an intermediate tooth space regionof the tooth ring of the same sprocket, the material contributing to thetooth, for example, a portion of the tooth base, can be used to connectthe connection means to the smaller of the two adjacent sprockets,independently of whether the connection means is constructed integrallyor separately with respect to the smaller of the two sprockets.

If the torque transmission from the bicycle chain to the rear runningwheel is carried out via the sprocket having the largest diameter, theconnectors—irrespective of whether they are constructed separately fromthe sprockets which they connect or integrally therewith—can beconstructed to be particularly thin if the longitudinal end thereofwhich is located nearer the sprocket having the larger diameter leadsthe opposite longitudinal end, which is located nearer the axiallydirectly adjacent sprocket in the sprocket having the smaller diameter,in the drive rotation direction of the sprocket arrangement.

In an embodiment, a bicycle rear wheel sprocket arrangement which isrotatable about a sprocket rotation axis and which has a plurality ofsprockets which are coaxial with respect to the sprocket rotation axisand which are arranged with axial spacing from each other and which havedifferent numbers of teeth which are constructed for positive-lockingengagement with a bicycle chain, have features as are claimed herein.For implementing the advantages of the sprocket having the largestdiameter mentioned in the claims, important aspects may involvecharacteristics besides the implementation of the gear range packingcoefficient mentioned in the introduction. The use of the sprocket whichhas the largest diameter and which is described in the features of theclaims makes it easier to implement a bicycle rear wheel sprocketarrangement with the values mentioned for the gear range packingcoefficient. Therefore, the present invention also relates to a bicyclerear wheel sprocket arrangement which can be rotated about a pinionrotation axis and which has a plurality of sprockets which are coaxialwith respect to the sprocket rotation axis and which are arranged withaxial spacing from each other and which have different numbers of teethwhich are constructed for positive-locking engagement with a cyclechain, wherein the pinion arrangement has features of the claimedcharacteristics.

In an embodiment, a bicycle rear wheel drive arrangement is providedhaving a bicycle rear wheel sprocket arrangement which is constructed asdescribed above and having a bicycle chain.

As already indicated above, there may be produced undesirable effects atthe sprocket having the smallest diameter as a result of the obliqueposition of the chain. For example, rubbing of the chain on the axiallyadjacent, next-largest sprocket. In this instance, the axial guiding ofthe chain and therefore the limitation of the chain movement in an axialdirection on the sprocket having the smallest diameter is of particularinterest. That axial guiding of the chain on the sprocket having thesmallest diameter can be improved and therefore the axial movability ofthe chain on the sprocket can be limited in that the tooth ring at leastof the sprocket having the smallest diameter of the bicycle rear wheelsprocket arrangement is constructed so as to have an axial sprocketthickness which changes over a periphery in a peripheral directionbetween teeth and intermediate tooth spaces which are directly adjacentthereto. Consequently, there can be constructed on the sprocket axiallythicker regions which then axially guide the bicycle chain when thebicycle chain meshes with the sprocket having the smallest diameter. Inthe axially thinner regions of the sprocket, however, there may beprovided axial play between the bicycle chain and sprocket portions inorder to keep friction effects which act between the bicycle chain andthe sprocket small. Since the bicycle chain has a periodic structure inthe longitudinal chain direction, the variable axial sprocket thicknessis preferably also constructed to be periodically variable.

In order to allow an introduction of the sprocket teeth with as littleloss as possible in intermediate spaces of the bicycle chain providedfor this purpose and a withdrawal of the sprocket teeth out of thoseintermediate spaces in a similarly loss-free manner, the axial thicknessof the sprocket in the region of the intermediate tooth spaces isadvantageously greater than in the region of the teeth. The sprocketconfigured in this manner axially guides the bicycle chainadvantageously only in the region of the intermediate tooth spaces whilethe teeth of the sprocket in the force-transmitting engagement with thebicycle chain between plate pairs of the bicycle chain are used only forforce transmission between the rollers of the bicycle chain and thesprocket.

The bicycle chain may be a roller chain which is known per se and whichhas a plurality of rollers which are arranged in an equidistant mannerin the longitudinal chain direction with parallel roller rotation axes,which rollers are connected to each other alternately via pairs ofparallel inner plates and outer plates, wherein each inner plate isarranged between the roller and an outer plate in the region of a rollerconnected thereto in the direction of the roller rotation axis.

In such a bicycle chain, it is already advantageous for reasons ofweight for both the outer plates and the inner plates to have a smallerheight in a longitudinal center portion than in the longitudinal endportions thereof.

In an embodiment, an arrangement of the above-mentioned connection meansin order to connect two axially adjacent sprockets can be carried outadvantageously in a position which is radially as far outwards aspossible if the connection means are connected radially in a position sofar outwards with the two axially adjacent sprockets that a radiallyinner edge of the longitudinal end regions of the inner plates and/orouter plates is located nearer the sprocket rotation axis than aradially outer edge of the connection means during a meshing engagementof the bicycle chain with the smaller of the two axially adjacentsprockets.

For more precise axial guiding of the bicycle chain, at least at thesprocket having the smallest diameter, substantially through theintermediate tooth space regions of the sprocket with minimal axialmovement play of the bicycle chain on the sprocket, it is advantageous,at least for the sprocket having the smallest diameter, for the axialwidth of a roller support face of the sprocket, which support face isconfigured for abutting engagement with a roller of the bicycle chain inthe region of an intermediate tooth space, deviates by no more than 10%from the axial dimension of an outer roller face—in relation to theaxial dimension of the outer roller face—configured for abutment withthe roller support face. The better the axial dimensions of the rollersupport face of the sprocket and the outer roller face adjoining itcorrespond, the more precisely the bicycle chain can be guided on thesprocket. In an embodiment, the axial width of the roller support facedeviates by no more than 5%, particularly preferably by no more than 3%,from the axial dimension of the outer roller face.

During a meshing engagement with the at least one sprocket, inparticular the sprocket having the smallest diameter, an inner platepair generally has an internal inner plate which is located axiallynearer the axial end of the sprocket arrangement with the sprockethaving the largest diameter and has an external inner plate which islocated axially nearer the axial end of the sprocket arrangement withthe sprocket having the smallest diameter. Longitudinal center portionsof the internal and external inner plate of the inner plate pair arethen located in the longitudinal chain direction between two rollerswhich are directly connected to that inner plate pair, wherein anintroduction portion of a tooth is introduced between the longitudinalcenter portions, and is withdrawn again during a torque transmissionfrom the bicycle chain to the sprocket which meshes therewith.

In order to prevent undesirable friction between the introductionportion of a tooth and the bicycle chain, in particular in the region ofthe axially nearer internal plates of the inner plate pairs, in anembodiment at least one tooth, for example a plurality of teeth,preferably for all the teeth, of the sprocket having the smallestdiameter, that the axial width of the introduction portion of the atleast one tooth is smaller than a clear axial width of the longitudinalcenter portions of the external and internal inner plates from eachother so that, during the torque transmission, the end face directedaway from the sprocket having the largest diameter, with respect to theintroduction portion which is introduced between the longitudinal centerportions, is arranged to be separated by an axial gap from thelongitudinal center portion of the external inner plate of the innerplate pair, which inner plate is axially opposite it.

In order to ensure that at least the sprocket having the smallestdiameter axially guides the bicycle chain which meshes with therespective sprocket only in the peripheral portions between directlysuccessive teeth (intermediate tooth spaces), and in order to furtherprevent undesirable friction and therefore power losses during riding ofthe bicycle, the axial sprocket width in the region of the tooth base ispreferably smaller radially inside the introduction portion than theclear axial width between the edges of the parallel inner plates of eachinner plate pair in the longitudinal center portion(s), which edges facethe sprocket rotation axis, so that an edge of the longitudinal centerportion of the external inner plate, which edge faces the sprocketrotation axis, is also arranged to be separated during the torquetransmission by a gap from a tooth base of an introduction portion whichis introduced between them.

In order to achieve the advantageous effects in conjunction with thesprocket having the smallest diameter, various important aspects areprovided beyond the characteristics described with the use of thepreviously described sprocket having the largest diameter and theimplementation of the values of the gear range packing coefficientdescribed in the introduction so that the present invention also relatesto a bicycle rear wheel drive arrangement having a bicycle rear wheelsprocket arrangement and having a bicycle chain, wherein the tooth ringat least of the sprocket having the smallest diameter of the bicyclerear wheel sprocket arrangement is constructed so as to have an axialsprocket thickness which changes, in particular which changesperiodically, over a periphery in a peripheral direction between teethand intermediate tooth spaces which are directly adjacent thereto,wherein the axial thickness of the sprocket is greater in the region ofthe intermediate tooth spaces than in the region of the teeth, whereapplicable with the inclusion of the characterising features of variousclaims made herein.

The embodiments described herein may relate to a bicycle drivearrangement having a bicycle rear wheel sprocket arrangement or abicycle rear wheel drive arrangement, in particular having a rear wheelsprocket arrangement, as described above and/or having a rear wheelsprocket arrangement as described above and having precisely one frontchain ring which is nearer the tread crank, wherein the chain ring has atechnically effective number of teeth between 30 and 40, preferablybetween 34 and 36, with the limits mentioned being included. The“effective” number of teeth is the number of teeth of the chain ringitself in the case of a chain ring connected directly to the treadcranks. If, however, the chain ring is connected to the tread cranks viaa gear arrangement, for example, a planet gear, the effective number ofteeth of the chain ring results from the actual number of teeth of thechain ring taking into consideration the transmission ratio of the geararrangement provided in the force path between the tread cranks andtooth ring of the chain ring. The effective number of teeth of a chainring which is connected to the tread cranks by means of a geararrangement is the number of teeth which a chain ring which is connecteddirectly—therefore, without a gear arrangement being interposed—to thetread cranks and which brings about an identical torque transmissionfrom the tread cranks to the same rear wheel sprocket would have.

With the rear wheel sprocket arrangement, that is to say, with thenumber of sprockets present therein and the respective number of teeththereof, objective technical circumstances are provided for traveloperation in the most optimised manner possible, such as, for example,the possible transmission bandwidth and the graduation of the individualadjustable transmission ratios.

However, physical/individual characteristics of the individual cyclistare extremely different. Even cyclists with substantially the same treadpower can produce different tread frequencies and different tread forceswhile they output the same tread power.

The individualised adaptation of the objective technical transmissioncircumstances provided by the rear wheel sprocket arrangement isconsequently carried out advantageously by associating a chain ringtaking into consideration the physical preferences of the respectivecyclist with the rear wheel sprocket arrangement. For theabove-described rear wheel sprocket arrangement, consequently, a chainring having a technically effective number of teeth between 30 and 40forms a large number of individual preferences of different cyclists,such as, for example, tread frequencies and the like. Consequently, abicycle can very readily be constructed by provision with the rear wheelsprocket arrangement according to the invention in principle for aspecific bandwidth of transmission ratios and a similarly determinedgraduation there-between, and individualised by the selection only ofthe suitable chain ring for the respective type of rider.

In comparison with the currently leading single derailleur chainswitching system “XX1”, for example, the rear wheel sprocket having thelargest diameter of the sprocket arrangement according to embodimentsdescribed herein may have eight more teeth and the chain ring may haveat least four more teeth. Consequently, not only is an even smallertransmission ratio achieved between the tread crank and rear wheel, butfurthermore the maximum occurring tensile loading of the bicycle chaincan be substantially reduced with the drive power otherwise being thesame by using sprockets and chain rings which generally have largerdiameters.

Furthermore, in the case of an unchanged sprocket having the smallestdiameter, an even greater—in comparison with the prior art—maximumtransmission ratio can also be adjusted as a result of theabove-mentioned increase of the number of teeth of the chain ring withrespect to the prior art (e.g. “XX1”). Sprocket wheel construction mayallow post-processing and further processing in a particularly simple,time-saving and advantageous manner. In an embodiment, a sprocket wheelcan be stacked on another sprocket wheel of the same configuration insuch a way that the first area of the first main surface of the sprocketwheel rests over an extended area on the first area of the second mainsurface of the other sprocket wheel, and that the second area of thefirst main surface of the sprocket wheel rests over an extended area onthe second area of the second main surface of the other sprocket wheel.

In FIGS. 1 to 3, an embodiment of a bicycle rear wheel sprocketarrangement is generally designated 10. The sprocket arrangement 10 hasin the example illustrated 12 sprockets which are designated 12 to 34.The sprocket having the largest diameter in this instance has thereference numeral 12, the next-smallest sprockets which follow in thedirection of the sprocket axis R have the reference numerals 14 to 34,wherein the sprocket having the smallest diameter of the sprocketarrangement 10 is designated 34.

In this instance, the sprockets 14 to 34 are constructed as a sprocketdome 36 in a materially coherent, integral manner. The sprocket dome 36is supported on a dome carrier 38 which can be connected to a bicyclehub which is not illustrated. Only the sprocket 12 having the greatestdiameter is constructed separately from the remaining 11 sprockets 14 to34.

In this embodiment, the sprocket 34 having the smallest diameter has 10teeth and the sprocket 12 having the largest diameter has 50 teeth. Fromthe sprocket 34 having the smallest diameter to the sprocket 12 havingthe largest diameter, the sprockets of the sprocket arrangement 10 havethe following numbers of teeth: 10-12-14-16-18-21-24-28-32-36-42-50.Consequently, the largest percentage increase in the number of teethoccurs from the smallest sprocket 34 to the next largest sprocket 32.That increase in the number of teeth is 20% in relation to the number ofteeth of the sprocket 34 having the smallest diameter. All the remainingincreases in the number of teeth from one sprocket to the next-largestsprocket are smaller than 20% in percentage terms. A fine graduation ofthe transmission ratios which can be provided with the sprocketarrangement 10 is thereby achieved.

The gear range quotient of the sprocket arrangement 10 is consequently50:10=5.

The integral construction of the sprocket dome 36 will be explained byway of example below with reference to the axially directly adjacentsprockets 24 and 26:

An axial gap 37 which is bridged by a web 39 is provided between thesprockets 24 and 26. The web 39 is integrally constructed both with thesprocket 24 and with the sprocket 26. The web 39 may be constructed, forexample, by material regions which were originally located before andafter the web in a peripheral direction being removed, for example, bymilling, so as to leave the web.

As can be seen in particular in the example of the sprocket 26, in whichthe plane of section of FIG. 1 cuts through a tooth, the web 39—as arealso all the remaining webs 39 of the sprocket dome 36—is connected at aperipheral position to the smaller sprocket 26, at which a tooth is alsoconstructed. This allows a construction of the web 39 in the positionradially as far outwards as possible, which generally increases therigidity of the sprocket dome 36. All the sprockets 14 to 34, which areintegrally coherent in the same manner, of the sprocket dome 36 have asolid tooth ring 35, on which the teeth of the respective sprocket andthe webs 39 are constructed.

As is typical for sprockets, the sprocket 12 having the largest diameteralso has in a radially outermost position a tooth ring 40 which ispreferably solid in a peripheral direction and, in a radially innermostposition, a hub region 42 which is also solid preferably in a peripheraldirection. The tooth ring 40 is constructed to move into meshingengagement with a bicycle chain in order to transmit torque by means ofthe bicycle chain (not shown in FIGS. 1 to 3 from the tread cranks (alsonot illustrated) of a bicycle to the sprocket arrangement 10.

The hub region 42 is used to transmit torque from the sprocketarrangement 10 to the rear wheel hub which is not illustrated in theFigures and therefore to the rear running wheel of the bicycle which isnot illustrated.

In order to change the sprocket which meshes with the bicycle chainwhich is not illustrated, the sprocket arrangement 10 cooperates with aratchet gear which is also not illustrated in the Figures. The ratchetgear is moved in this instance with a travel path which has an axialcomponent in the direction of the sprocket rotation axis R, beyond theaxial extent range of the sprocket arrangement 10. The axial positionsof the ratchet gear relative to the sprocket arrangement 10, at whichthe ratchet gear remains near the chain-guiding sprocket, are orientatedtowards the front faces of the sprockets. In the present example, thefront faces are orientated orthogonally relative to the sprocketrotation axis R wherein the radially outermost front face is intended tobe used on each sprocket. In this instance, the front face is theradially outermost front face portion of a sprocket, which portion isorthogonal to the sprocket rotation axis R and is located at the frontside directed towards the next-smallest sprocket or, in the case of thesprocket 34 having the smallest diameter, at the front side directedaway from the sprocket 12 having the largest diameter.

In the case of the sprocket 12 having the largest diameter, the frontface 44 is constructed at the front side of the tooth ring 40 directedtowards the sprocket 34 having the smallest diameter. In the case of thesprocket 34 having the smallest diameter, the front face 46 thereof isconstructed at the tooth flanks at the front side of the sprocket 34directed away from the sprocket 12 having the largest diameter.

The axial spacing A between the front faces 44 and 46 of the sprocket 12having the largest diameter or the sprocket 34 having the smallestdiameter is 40.5 mm in the example illustrated.

Therefore, the packing density quotient of the sprocket arrangement 10is 12:40.5=0.296.

Therefore, the gear range packing coefficient of the sprocketarrangement 10 is 5×0.296=1.48.

With the sprocket arrangement 10, therefore, it is possible to managewith only a single chain ring on the tread cranks even on a mountainbike which is constructed for very steep gradients. In this instance, asingle chain ring having an effective number of teeth in the range from30 to 40 teeth is preferably used. Consequently, a speed step-down isbrought about from the chain ring to the sprocket 12 having the largestdiameter and a speed step-up is brought about from the chain ring to thesprocket 34 having the smallest diameter. As a result of thealways-valid energy conservation, torque is stepped up from the chainring to the sprocket 12 having the largest diameter and is stepped downwith respect to the sprocket 34 having the smallest diameter. Thestep-up and step-down are referred to in the present application withthe general term “transmission”.

In order to be able to produce the above-mentioned spacing A between thefront faces 44 and 46 in the region of the tooth rings of the sprockets12 to 34 without a similarly large axial spacing having to be providedfor the assembly of the sprocket arrangement 10 in the region of therear wheel hub, that is to say, for instance at the hub region 42 of thesprocket 12, the sprocket 12 having the largest diameter in the exampleillustrated has an angled portion 47 substantially in the region of theradial center thereof (always measured from the sprocket rotation axisR). Therefore, a sprocket region of the sprocket 12 having the largestdiameter, which region is located radially inside the angled portion 47,is nearer the sprocket 34 having the smallest diameter than a sprocketregion of the sprocket 12 located radially outside the angled portion47.

As can further be seen in FIG. 1, the sprocket 12 having the largestdiameter is supported with the front face 44 thereof on axialprojections 48 of the next-smallest sprocket 14 which is directlyaxially adjacent thereto. The axial projections 48 are constructed inthe example illustrated in an integral materially cohesive manner withthe sprocket 14. However, this does not have to be the case. In place ofthe integral axial projections 48, there may also be provided betweenthe sprockets 12 and 14 axial spacers which are constructed separatelyfrom the sprockets 12 and 14 in order to bridge the axial gap 50 presentbetween those sprockets.

FIG. 2 is a front view in a viewing direction along the sprocketrotation axis R towards the sprocket arrangement 10 of FIG. 1.Consequently, the viewer is looking at FIG. 2 towards the front faces 44and 46 of the sprocket 12 having the largest diameter or the sprocket 34having the smallest diameter and towards all the front faces of theremaining sprockets 14 to 32, but which are not indicated in greaterdetail in FIG. 2. FIG. 2 shows front-end indentations or recesses 52 inthe front face 44 of the sprocket 12 having the largest diameter. Thoserecesses 52 act as an auxiliary switching means during switching fromthe sprocket 14 to the larger sprocket 12.

FIG. 3 is a rear view in a viewing direction opposite the viewingdirection of FIG. 2. Therefore, FIG. 3 shows some details of thestructural configuration of the sprocket 12 having the largest diameter,which details promote the configuration of the sprocket arrangement 10with the gear range packing coefficient demonstrated.

As FIG. 2 has already shown, the sprockets 14 to 34 of the sprocket dome36 are produced using a skeleton construction, that is to say, withsolid radially outer tooth rings, on which the teeth and intermediatetooth spaces are formed, and with the spoke-like webs 39 radially insidethe tooth rings.

Thus, the sprocket 12 having the largest diameter is also formedradially externally between the solid tooth ring 40 and the similarlysolid hub region 42 radially internally so as to have sprocket spokes inorder to reduce the weight of the sprocket 12 having the largestdiameter without substantial losses of rigidity.

In the present example, the sprocket 12 having the largest diameter hasa radially internal spoke region 54 and a radially external spoke region56. The radially internal spoke region 54 has a smaller number ofsprocket spokes 58 than the radially external spoke region 56. Theradially internal and the radially external spoke region 54 and 56 aredelimited from each other by a solid intermediate ring region 60 whichis preferably constructed in an annular manner around the sprocketrotation axis R. The construction of the intermediate ring region 60allows the different number of sprocket spokes in the spoke regions 54and 56.

As a comparison of FIGS. 1 and 3 with each other shows, the angledportion 47 is constructed in the solid intermediate ring region 60 sothat the angled portion is completely constructed in a radial region ofsolid material. It is thereby possible for the sprocket spokes to beconstructed at both sides of the angled portion 47 or at both sides ofthe intermediate ring region 60 as planar sprocket spokes, which isadvantageous for the rigidity and dimensional stability thereof underload.

In order to differentiate them from the sprocket spokes 58 of theradially internal spoke region 54, the sprocket spokes of the radiallyexternal spoke region 56 are designated 62 and 64.

The drive rotation direction of the sprocket arrangement 10 andtherefore of the sprocket 12 having the largest diameter is designated Min FIGS. 2 and 3.

In this instance, every second sprocket spoke 62 of the outer spokeregion 56 is connected to the sprocket spoke 64 which leads it directlyin a drive rotation direction M by a connection strut 66. The rigidityof the sprocket 12 having the largest diameter is increased by thatconnection strut 66 over-proportionally relative to the increase inweight connected therewith. Consequently, the sprocket spokes 62 areconnection spokes in the sense of the above introduction to thedescription. In order to avoid an unnecessary weight increase, thesprocket spokes 64 are not connected with connection struts to thesprocket spokes 62 which lead them directly in the drive rotationdirection M.

The connection struts 66 are preferably located on a circle whose centeris the sprocket rotation axis R. The connection struts 66 are furtherlocated on the sprocket 12 in the radially outermost position but withinthe radial extent range of the axially directly adjacent, next-smallestsprocket 14. The next-smallest sprocket 14 and with it the sprocket dome36 can thereby be or become mechanically connected at the connectionstruts 66 to the sprocket 12 having the largest diameter.

The axial projections 48 previously mentioned in connection with FIG. 1are preferably supported with the end faces thereof directed away fromthe sprocket 14 on the sides of the connection struts 66 facing them. Ina particularly advantageous manner, pins 68 which may be integrallyformed with the axial projections 48 thereon extend through theconnection struts 66 in the example illustrated. By means of those pins68 acting as connection means, the sprocket 12 having the largestdiameter is connected so as to transmit torque and axial force to thenext-smallest sprocket 14 and therefore to the entire sprocket dome 36.

As can very clearly be seen in FIG. 3, all the sprocket spokes 58, 62and 64 of the sprocket 12 having the largest diameter are constructed onthat sprocket 12 in such a manner that the radially inner longitudinalends thereof are leading with respect to the radially outer longitudinalends of the same sprocket spoke in the drive rotation direction M. Apreponderant compression or pressure loading of the individual sprocketspokes 58, 62 and 64 is thereby achieved during a torque transmissionfrom a bicycle chain to the rear wheel hub.

Not only do the radially inner longitudinal ends of a sprocket spokelead the radially outer longitudinal end of the same spoke but inaddition the sprocket spokes 58, 62 and 64 may be constructed not to bestraight but instead curved. The curvature of the sprocket spokes 58, 62and 64 is brought about in this instance about curvature axes which areparallel with the sprocket rotation axis R and which follow the curvedsprocket spoke in a drive rotation direction M. Therefore, the sprocketspokes 58, 62 and 64 are curved in a concave manner when viewed in thedrive rotation direction M and are curved in a convex manner when viewedcounter to the drive rotation direction M. As a result of thiscurvature, in the event of a torque transmission from the tooth ring 40to the hub region 42 and therefore to the rear wheel hub, there isachieved in the sprocket spokes 58, 62 and 64 a particularlyadvantageous stress loading which is primarily formed by pressurestresses. The pressure resistance of a sprocket spoke is many timesgreater than the tensile resistance or shearing resistance thereof.

Furthermore, the curvature mentioned causes the angle α, which a tangent70 located in the sprocket plane of the sprocket 12 on a sprocket spoke58, 62 or 64 encloses with a tangent 72 also located in the sprocketplane on a reference circle 74 with the sprocket rotation axis R as thecenter, to be increasingly great the smaller the radius of the referencecircle is. Preferably, all the angles between spoke tangents andreference circle tangents are of the same size for one and the samereference circle at all the sprocket spokes cut by this referencecircle. In principle, the angle condition described in this instancecould also be complied with by sprocket spokes in the form of polygons.However, the above-described curved construction of the sprocket spokesmay be preferable in order to prevent stress peaks in corner regions orbent regions of sprocket spokes in the form of polygons.

FIG. 4 is a front view of the sprocket 34 having the smallest diameterwhen viewed in an axial direction. Consequently, the sprocket rotationaxis R is orthogonal to the plane of the drawing of FIG. 4 and thesprocket 12 which has the largest diameter and which is not illustratedin FIG. 4 and all the other sprockets 14 to 32 are behind the plane ofthe drawing of FIG. 4.

FIG. 4 illustrates a portion of a bicycle chain 76 which meshes with thesprocket 34 having the smallest diameter. The bicycle chain 76 has pairs78 of outer plates and pairs 82 of inner plates in an alternating mannerover the course thereof. In FIG. 4, the viewer is looking towards theexternal outer plate 80, that is to say, the plate located further awayfrom the sprocket 12 having the largest diameter. Similarly, the vieweris looking towards the external inner plate 84 in the inner plate pair82. Furthermore the outer plate pairs 78 and inner plate pairs 82 whichare successive in an alternating manner in the longitudinal chaindirection are connected to each other so as to be rotatable relative toeach other about a chain link axis K. The chain link axes K of eachconnection between successive outer plate pairs 78 and inner plate pairs82 are ideally parallel with the sprocket rotation axis R during meshingengagement with the sprocket 34. Furthermore, the chain link axes K arerotation axes of rollers 86 which are received between the respectiveplate pairs 78 and 82. However, the rollers 86 are hidden in FIG. 4 bythe outer plates 80 and 84, respectively, and can be seen only in FIGS.5 and 6.

Sprocket teeth 88 which are arranged so as to be distributedequidistantly at the periphery of the sprocket 34 engage in theintermediate spaces between two rollers 86 which are successive in thelongitudinal chain direction in order to transmit torque between thebicycle chain 76 and the rear running wheel. In this instance, therollers 86 are positioned on the sprocket 34 in the region of theintermediate tooth spaces 90 between teeth 88 which are directlysuccessive in a peripheral direction.

Of the teeth 88, only an introduction portion 94 is introduced, duringmeshing engagement with the bicycle chain 76, into the intermediatespace between two plates of one and the same plate pair and is withdrawntherefrom again. As will be further illustrated in detail in connectionwith the following FIGS. 5 and 6, the introduction portion 94 isconstructed to be less wide in an axial direction than a support portion95 of the sprocket 34 located radially inside the introduction portions.At the transition between the axially thicker support portion 95 and theaxially thinner introduction portion 94, there is located an axial step92 which further indicates the position of the respective tooth base.The axial step 92 may be constructed as a chamfer which is inclined inan axial direction away from the sprocket 12 having the largest diametertowards the sprocket rotation axis R.

FIG. 4 indicates on the inner plate pair 82 a longitudinal centerportion L of the inner plate pair 82 and therefore of the external innerplate 84 and the internal inner plate opposite it in an axial direction.

The plates of the inner plate pairs 82 and the outer plate pairs 78 havea smaller plate height h in the longitudinal center portion L thereofthan in the longitudinal end regions E thereof. Consequently, a web 39for connection to the next-largest sprocket 32 (indicated by thebroken-line rectangle 39 in FIG. 4) at the peripheral location of atooth 88 may be provided in such a radially outer position that theradially outer edge 39 a thereof is further away from the sprocketrotation axis R than an edge 97 of a plate in the region of thelongitudinal end regions E thereof, which edge 97 faces the sprocketrotation axis R.

FIG. 5 is a cross-section of the engagement situation of the sprocket 34with the chain 76 in the plane of section V-V which contains thesprocket rotation axis R. The cross-section shown in FIG. 5 furtherextends through the chain link axis K and therefore through a roller 86of the bicycle chain 76.

FIG. 5 shows how the support portion 95 of the sprocket 34 axially leadsthe bicycle chain 76 in the region of an intermediate tooth space 90 andconsequently limits the axial movability thereof along the sprocketrotation axis R. In this instance, a roller 86 is preferably positionedwith the outer face 86 a thereof on a corresponding support face 95 a ofthe support portion 95 directed in a radial direction, wherein thesupport portion 95, at least in the support region of the support face95 a thereof which is constructed for abutment of an outer roller face86 a, deviates from the axial width of the roller 86 which abuts it inthe event of engagement in terms of the axial width thereof by no morethan 10%, preferably no more than 5%, particularly preferably by no morethan 3%. The axial width of the roller 86 is the reference variable forthe percentage deviation.

The view of FIG. 5 shows a portion of an internal inner plate 85 whichaxially retains the roller 86 between the inner plate pair 82 togetherwith the external inner plate 84. The chain link which is formed alongthe roller axis of the roller 86 which coincides with the chain linkaxis K comprises a chain rivet 87 which connects the plate pairs whichmeet each other at the chain link and which comprise the outer platepair 78 and inner plate pair 82 to each other in an axial direction, butallows a relative rotation about the chain link axis K as the onlyrelative movement.

The inner plates 84 and 85 each have in the longitudinal section of FIG.5 an axial member 84 a and 85 a which is surrounded by the roller 86 andhave a radial member 84 b and 85 b (not illustrated), between which theroller 86 is axially chamfered. Consequently, the radial members 84 band 85 b of the inner plates 84 and 85 are opposite the front sides ofthe roller 86. It is the radial members 84 b and 85 b of the innerplates 84 and 85 which also bring about axial fixing of the bicyclechain 76 to the sprocket 34 in conjunction with the support portion 95.The radial members are discs and the axial members are sleeves in termsof the three-dimensional shape thereof.

FIG. 6 is a longitudinal section in the plane of section VI-VI whichcontains the sprocket rotation axis R. That plane of section intersectswith the longitudinal center portion L of an inner plate pair 82 andintersects with the tooth 88 of the sprocket 34 introduced into thatlongitudinal center portion L.

The roller 86 shown in FIG. 6 adjoins the tooth which leads the cuttooth 88 of FIG. 6 and transmits torque thereto. A roller which adjoinsthe cut tooth 88 of FIG. 6 for the purpose of torque transmission is infront of the plane of the drawing of FIG. 6 and is therefore notillustrated.

As can be seen in FIG. 6, the axial width of the introduction portion 94of the tooth 88 has smaller dimensions than the clear width of thelongitudinal center portion L of the inner plate pair 82 so that theside of the introduction portion 94 having the front face 46—that is tosay, the side directed away from the sprocket 12 having the largestdiameter—is located with spacing from the external inner plate 84 of theinner plate pair 82 opposite it. Consequently, an axial gap 96 isprovided between the introduction portion 94 and the external innerplate 84 axially opposite it. This axial gap 96 ensures the axialmovability which the bicycle chain 76 requires in order to be switchedto the next-largest sprocket. Therefore, a movability which issufficient for switching is achieved in respect of the chain 76 incooperation with the above-described, axial guiding of the bicycle chain76 in the intermediate tooth spaces 90 without an undesirable rubbingcontact of the chain 76 with the next-largest sprocket being produced asa result of excessively oblique running of the chain 76.

FIG. 6 further illustrates that an edge 97 of the external inner plate84 directed towards the sprocket rotation axis R is arranged withspacing from the step 92 so that there is also a gap 99 between the step92 and the edge 97 of the external inner plate 84 nearer the sprocketrotation axis R. Consequently, at least the external inner plate 84 ofthe inner plate pair 82 has no contact with the tooth 88 which engagesbetween the inner plate pair 82. Consequently, the tooth 88 isadvantageously used only or practically only for transmitting torquebetween the bicycle chain 76 and the sprocket 34, whereas theintermediate tooth spaces 90 can be used predominantly or even only foraxially guiding the bicycle chain 76 on the sprocket 34.

As a result of this structural configuration, the bicycle chain 76 canbe guided in an axially taut manner on the sprocket 34 so that thebicycle chain 76 does not touch the next-largest sprocket 32 which isaxially directly adjacent to the sprocket 34 even in the presence ofonly a single chain ring at the tread crank side and the associatedoblique position. This is even more noteworthy since, in the twelve-foldsprocket arrangement 10 shown by way of example, the front face spacingbetween the sprockets 32 and 34 is very small and, for example, may beonly approximately 3.6 mm.

The illustrations of the embodiments described herein are intended toprovide a general understanding of the structure of the variousembodiments. The illustrations are not intended to serve as a completedescription of all of the elements and features of apparatus and systemsthat utilize the structures or methods described herein. Many otherembodiments may be apparent to those of skill in the art upon reviewingthe disclosure. Other embodiments may be utilized and derived from thedisclosure, such that structural and logical substitutions and changesmay be made without departing from the scope of the disclosure.Additionally, the illustrations are merely representational and may notbe drawn to scale. Certain proportions within the illustrations may beexaggerated, while other proportions may be minimized. Accordingly, thedisclosure and the figures are to be regarded as illustrative ratherthan restrictive.

While this specification contains many specifics, these should not beconstrued as limitations on the scope of the invention or of what may beclaimed, but rather as descriptions of features specific to particularembodiments of the invention. Certain features that are described inthis specification in the context of separate embodiments can also beimplemented in combination in a single embodiment. Conversely, variousfeatures that are described in the context of a single embodiment canalso be implemented in multiple embodiments separately or in anysuitable sub-combination. Moreover, although features may be describedabove as acting in certain combinations and even initially claimed assuch, one or more features from a claimed combination can in some casesbe excised from the combination, and the claimed combination may bedirected to a sub-combination or variation of a sub-combination.

One or more embodiments of the disclosure may be referred to herein,individually and/or collectively, by the term “invention” merely forconvenience and without intending to voluntarily limit the scope of thisapplication to any particular invention or inventive concept. Moreover,although specific embodiments have been illustrated and describedherein, it should be appreciated that any subsequent arrangementdesigned to achieve the same or similar purpose may be substituted forthe specific embodiments shown. This disclosure is intended to cover anyand all subsequent adaptations or variations of various embodiments.Combinations of the above embodiments, and other embodiments notspecifically described herein, are apparent to those of skill in the artupon reviewing the description.

The Abstract of the Disclosure is provided to comply with 37 C.F.R. §1.72(b) and is submitted with the understanding that it will not be usedto interpret or limit the scope or meaning of the claims. In addition,in the foregoing Detailed Description, various features may be groupedtogether or described in a single embodiment for the purpose ofstreamlining the disclosure. This disclosure is not to be interpreted asreflecting an intention that the claimed embodiments require morefeatures than are expressly recited in each claim. Rather, as thefollowing claims reflect, inventive subject matter may be directed toless than all of the features of any of the disclosed embodiments. Thus,the following claims are incorporated into the Detailed Description,with each claim standing on its own as defining separately claimedsubject matter.

It is intended that the foregoing detailed description be regarded asillustrative rather than limiting and that it is understood that thefollowing claims including all equivalents are intended to define thescope of the invention. The claims should not be read as limited to thedescribed order or elements unless stated to that effect. Therefore, allembodiments that come within the scope and spirit of the followingclaims and equivalents thereto are claimed as the invention.

1. A bicycle rear wheel sprocket arrangement which can be rotated abouta sprocket rotation axis, comprising: a plurality of sprockets which arecoaxial with respect to the sprocket rotation axis and are arranged withaxial spacing from each other and have different numbers of teeth whichare constructed for positive-locking engagement with a bicycle chain,the plurality of sprockets having: a gear range quotient which is formedby division of the number of teeth of a sprocket of the plurality ofsprockets having the largest diameter by the number of teeth of asprocket of the plurality of sprockets having the smallest diameter, anda packing density quotient formed by division of a number of sprocketsin the sprocket arrangement by the axial spacing measured in millimetersof axially outermost sprockets from each other, wherein the plurality ofsprockets has a gear range packing coefficient, formed from a product ofthe gear range quotient and the packing density quotient, which isgreater than 1.25 and two axially adjacent sprockets are constructedseparately from each other and are connected so as to transmit torque bya plurality of connectors which bridge an axial gap existing between theadjacent sprockets.
 2. The bicycle rear wheel sprocket arrangementaccording claim 1, wherein the sprocket having the largest diameter andthe sprocket which is axially directly adjacent thereto are constructedseparately from each other and are connected so as to transmit thetorque by a plurality of connection means which bridge the axial gapexisting between the adjacent sprockets.
 3. The bicycle rear wheelsprocket arrangement according claim 2, wherein a sprocket smaller thanthe sprocket having the largest diameter and a sprocket which is axiallydirectly adjacent thereto are constructed integrally with each other andare connected so as to transmit torque and preferably also so as totransmit axial force by a plurality of connectors in the form of webswhich bridge the axial gap existing between the adjacent sprockets. 4.The bicycle rear wheel sprocket arrangement according claim 3, whereinthe connectors are connected to the smaller of the two axially adjacentsprockets in a peripheral direction at a location at which a tooth islocated on the smaller of the two axially adjacent sprockets.
 5. Thebicycle rear wheel sprocket arrangement according claim 4, furthercomprising a bicycle chain that is a roller chain having a plurality ofrollers which are arranged in an equidistant manner in a longitudinalchain direction with parallel roller rotation axes, which rollers areconnected to each other alternately via pairs of parallel inner platesand outer plates, wherein each inner plate is arranged between theroller and an outer plate in a region of a roller connected thereto inthe direction of the roller rotation axis, and both the outer plates andthe inner plates have a smaller height in a longitudinal center portionthan in longitudinal end portions thereof.
 6. The bicycle rear wheelsprocket arrangement according claim 5, wherein the connection means areconnected radially in a position so far outwards with the smaller of thetwo axially adjacent sprockets that a radially inner edge of thelongitudinal end portions of the inner plates and/or outer plates islocated nearer the sprocket rotation axis than a radially outer edge ofthe connection means during a meshing engagement of the bicycle chainwith the smaller of the two axially adjacent sprockets.
 7. The bicyclerear wheel sprocket arrangement according claim 1, further comprising abicycle chain, wherein the tooth ring at least of the sprocket havingthe smallest diameter of the bicycle rear wheel sprocket arrangement isconstructed so as to have an axial sprocket thickness which changes, inparticular which changes periodically, over a periphery in a peripheraldirection between teeth and intermediate tooth spaces which are directlyadjacent thereto, wherein the axial thickness of the sprocket is greaterin a region of the intermediate tooth spaces than in a region of theteeth.
 8. The bicycle rear wheel sprocket arrangement according claim 7,wherein the tooth ring at least of the sprocket having the smallestdiameter of the bicycle rear wheel sprocket arrangement is constructedso as to have an axial sprocket thickness which changes periodicallyover a periphery in a peripheral direction between teeth andintermediate tooth spaces which are directly adjacent thereto.
 9. Thebicycle rear wheel sprocket arrangement according claim 8, wherein thebicycle chain is a roller chain that includes a plurality of rollerswhich are arranged in an equidistant manner in a longitudinal chaindirection with parallel roller rotation axes, which rollers areconnected to each other alternately via pairs of parallel inner platesand outer plates, wherein each inner plate is arranged between theroller and an outer plate in the region of a roller connected thereto inthe direction of the roller rotation axis, and at least for the sprockethaving the smallest diameter, it is the case that an axial width of aroller support face of the sprocket, which support face is constructedfor abutting engagement with a roller of the bicycle chain in the regionof an intermediate tooth space, deviates from an axial dimension of anouter roller face, in relation to the axial dimension of the outerroller face, constructed for abutment with the roller support face, byno more than 10%.
 10. The bicycle rear wheel sprocket arrangementaccording claim 9, wherein each inner plate is arranged between theroller and an outer plate in the region of a roller connected thereto inthe direction of the roller rotation axis, and at least for the sprockethaving the smallest diameter, it is the case that the axial width of aroller support face of the sprocket, which support face is constructedfor abutting engagement with a roller of the bicycle chain in the regionof an intermediate tooth space, deviates from the axial dimension of anouter roller face, in relation to the axial dimension of the outerroller face, constructed for abutment with the roller support face, byno more than 5%.
 11. The bicycle rear wheel sprocket arrangementaccording claim 10, wherein each inner plate is arranged between theroller and an outer plate in the region of a roller connected thereto inthe direction of the roller rotation axis, and at least for the sprockethaving the smallest diameter, it is the case that the axial width of aroller support face of the sprocket, which support face is constructedfor abutting engagement with a roller of the bicycle chain in the regionof an intermediate tooth space, deviates from the axial dimension of anouter roller face, in relation to the axial dimension of the outerroller face, constructed for abutment with the roller support face, byno more than 3%.
 12. The bicycle rear wheel sprocket arrangementaccording claim 11, wherein during a meshing engagement with at leastone sprocket, an inner plate pair has an internal inner plate which islocated axially nearer an axial end of the sprocket arrangement with thesprocket having the largest diameter and has an external inner platewhich is located axially nearer the axial end of the sprocketarrangement with the sprocket having the smallest diameter, whereinlongitudinal center portions of the internal and external inner plate ofthe inner plate pair are located in the longitudinal chain directionbetween two rollers which are directly connected to the inner platepair, wherein an introduction portion of a tooth is introduced betweenthe longitudinal center portions and is withdrawn again during a torquetransmission from the bicycle chain to the sprocket which meshestherewith, and for at least one tooth the axial width of theintroduction portion of the at least one tooth is smaller than a clearaxial width of the longitudinal center portions of the external andinternal inner plates from each other so that, during the torquetransmission, the end face directed away from the sprocket having thelargest diameter in respect of the introduction portion which isintroduced between the longitudinal center portions is arranged to beseparated by an axial gap from the longitudinal center portion of theexternal inner plate of the inner plate pair, which inner plate isaxially opposite it.
 13. The bicycle rear wheel sprocket arrangementaccording claim 12, wherein the axial width of an introduction portionof at least one tooth of the sprocket having the smallest diameter issmaller than a clear axial width of the longitudinal center portions ofthe external and internal inner plates from each other so that, duringthe torque transmission, the end face directed away from the sprockethaving the largest diameter in respect of the introduction portion whichis introduced between the longitudinal center portions is arranged to beseparated by an axial gap from the longitudinal center portion of theexternal inner plate of the inner plate pair, which inner plate isaxially opposite it.
 14. The bicycle rear wheel sprocket arrangementaccording claim 13, wherein in all teeth of at least the sprocket havingthe smallest diameter the axial width of the introduction portion of theat least one tooth is smaller than a clear axial width of thelongitudinal center portions of the external and internal inner platesfrom each other so that, during the torque transmission, the end facedirected away from the sprocket having the largest diameter in respectof the introduction portion which is introduced between the longitudinalcenter portions is arranged to be separated by an axial gap from thelongitudinal center portion of the external inner plate of the innerplate pair, which inner plate is axially opposite it.
 15. The bicyclerear wheel sprocket arrangement according claim 14, wherein an axialsprocket width in the region of a tooth base is smaller radially insidethe introduction portion than the clear axial width between thelongitudinal center portions of the inner plate pairs so that an edge ofthe longitudinal center portion of the external inner plate, which edgefaces the sprocket rotation axis, is also arranged to be separatedduring the torque transmission by a gap from a tooth base of anintroduction portion which is introduced between them.
 16. A bicyclerear wheel sprocket arrangement which can be rotated about a sprocketrotation axis, comprising: a plurality of sprockets which are coaxialwith respect to the sprocket rotation axis and are arranged with axialspacing from each other and have different numbers of teeth which areconstructed for positive-locking engagement with a bicycle chain, theplurality of sprockets having: a gear range quotient which is formed bydivision of the number of teeth of a sprocket of the plurality ofsprockets having the largest diameter by the number of teeth of asprocket of the plurality of sprockets having the smallest diameter, anda packing density quotient formed by division of the number of sprocketsin the sprocket arrangement by the axial spacing measured in millimetersof axially outermost sprockets from each other, wherein the plurality ofsprockets has a gear range packing coefficient, formed from a product ofthe gear range quotient and the packing density quotient, which isgreater than 1.25 and two axially adjacent sprockets are constructedseparately from each other and are connected so as to transmit an axialforce by a plurality of connectors which bridge an axial gap existingbetween the adjacent sprockets.
 17. The bicycle rear wheel sprocketarrangement according claim 16, wherein the sprocket having the largestdiameter and the sprocket which is axially directly adjacent thereto areconstructed separately from each other and are connected so as totransmit the axial force by a plurality of connection means which bridgethe axial gap existing between the adjacent sprockets.
 18. The bicyclerear wheel sprocket arrangement according claim 17, wherein a sprocketsmaller than the sprocket having the largest diameter and a sprocketwhich is axially directly adjacent thereto are constructed integrallywith each other and are connected so as to transmit torque andpreferably also so as to transmit axial force by a plurality ofconnectors in the form of webs which bridge the axial gap existingbetween the adjacent sprockets.
 19. The bicycle rear wheel sprocketarrangement according claim 18, wherein the connectors are connected tothe smaller of the two axially adjacent sprockets in a peripheraldirection at a location at which a tooth is located on the smaller ofthe two axially adjacent sprockets.
 20. The bicycle rear wheel sprocketarrangement according claim 19, further comprising a bicycle chain thatis a roller chain having a plurality of rollers which are arranged in anequidistant manner in a longitudinal chain direction with parallelroller rotation axes, which rollers are connected to each otheralternately via pairs of parallel inner plates and outer plates, whereineach inner plate is arranged between the roller and an outer plate inthe region of a roller connected thereto in the direction of the rollerrotation axis, and both the outer plates and the inner plates have asmaller height in a longitudinal center portion than in longitudinal endportions thereof.